Racing game with power accumulating means



March 11, 1969 c. NORMANDIN RACING GAME WITH POWER ACCUMULATING MEANS Sheet Filed NOV. 17, 1966 March 11, 1969 c. NORMANDIN RACING GAME WITH POWER ACCUMULATING MEANS z of 15 Sheet Filed Nov. 1'7, 1966 March 11, 1969 c. NORMANDIN RACING GAME WITH POWER ACCUMULATING MEANS Sheet Filed Nov. 17, 1966 March 11, 1969 c. NORMANDIN 3,432,167

RACING GAME WITH POWER ACCUMULATING MEANS Filed Nov. 17. 1966 Sheet 4 of 15 March 11, 1969 c. NORMANDIN RACING GAME WITH POWER ACCUMULATING MEANS Filed NOV. 17, 1966 Sheet INVEN TOR Cam/ IWDMAND/J/ 7 (a r d/ QM A6540 March 11 1969 RACING GAME WITH POWER ACCUMULATING MEANS Filed NOV. 17, 1966 Sheet 6 of 15 F I F 17 5918 9 lwvz/vrm j tam/fie MRMANDW AGDVT c. NORMANDIN 3,432,167

M h 11, 1969 c. NORMANDIN 3,432,167

RACING GAME WITH POWER AGCUMULATING MEANS Filed Nov. 17, 1966 Sheet 7 of 15 March 11, 1969 c. NORMANDIN 3,432,167

7 RACING GAME WITH POWER ACCUMULATING MEANS Filed Nov. 17. 1966 Sheet 8 of 15 .5 g. IO wvavrm cam/1: w/em/vu/v fML,

March 11, 1969 Q o m 3,432,167

RACING GAME WITH POWER ACCUMULATING MEANS Filed Nov. 17. 1966 Sheet 9 or 15 WIAIIIZIIIVA //V VE/VTOR CamzY/e March 11 1969 c. NORMANDIN 3,432,16

RACING GAME WITH POWER ACGUMULATING MEANS Filed Nov. 17, 1966 Sheet of 1s 107 .X/IIH I07 I08 l silk 17 I H6 I 8 l2| I04 .5... 02 H8 13 I25 IQ izlllulllluggulllllll 95 IO 95 March 11, 1969 c. NORMANDIN RACING GAME WITH POWER ACCUMULATING MEANS Sheet {1 of 15 Filed NOV. 17, 1966 lNVLNTOR Carmine Nor'mondir A e-n March 11, 1969 c. NORMANDIN RACING GAME WITH POWER ACCUMULA'IING MEANS A? of 15 Sheet Filed Nov. 17, 1966 \NVLNTOR C e ail No m n I B S W March 11, 1969 NORMANDW 3,432,167

RACING GAME WITH POWER ACCUMULATING MEANS Filed Nov. 17. 1966 Sheet /3 of 15' 9 iNVLNT OR 8 No m q li '7 Agent March 11, 1969 c, NORMANDW 3,432,167

RACING GAME WITH POWER ACCUMULATING MEANS Filed Nov. 17, 1966 Sheet 1 of 15 E] El [I [u U E] E1 4 E l6 I8 E] [:1 u can: u 1| :1 n 5 B ll! 4 17 'II l5 %n n'n m, J q ,t /r 23 9 2O 24 22 INVLNTOR C 0 alle Non mandi n 7 .59

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RACING GAME WITH POWER ACCUMULATING MEANS Filed Nov. 17, 1966' Sheet I5 of 15 Ell t lll:amm-

2 llllfl 29 6| I? 7 5 TX -1' 32 58 I 5? 32 3-5 NTOR Cami/ A ov-man /in United States Patent RACING GAME WITH POWER ACCUMULATING MEANS Camille Normandin, 301 Roy St., Sore], Quebec, Canada Filed Nov. 17, 1966, Ser. No. 595,126 US. Cl. 273-86 18 Claims Int. Cl. A63f 9/ 14 ABSTRACT OF THE DISCLOSURE This invention concerns a racing game in which the different racers are independently and individually controlled by competing players, means being provided to move the racers at at least two different sets of speeds, there being provided different speeds in each set, the speeds of one set being higher than the speeds of the other set, the racers, when running at said higher speeds, expending a reserve of energy which, when spent causes automatic slowing down of the racers to the lower set of speeds, the racers capable of accumulating energy only when running at said lower set of speeds.

The present invention relates to a game and, more particularly, to a racing game conceived to simulate what happens in a foot race, bicycle race or horse race when it is necessary to conserve energy for a sprint and/or a strong finish.

An object of the invention resides in the provision of a racing game of the character described, in which the players must use judgment and skill to determine the best time to place the racers in energy-accumulating position in order to run the racers at the maximum overall speed during the race.

Another object of the present invention resides in the provision of a racing game of the character described, in which one or more of the racers can be placed on automatic racing whereby a player can match this skill against these automatically run racers.

Another object of the present invention resides in the provision of means in a racing game of the character described, to adjust the racing capability of the individual racers in order to establish odds for the race.

Another object of the present invention resides in a racing game of the character described, in which mechanism is included to establish sprints during which the racers may run at a still higher set of speeds, but at only certain intervals during the race.

Another object of the present invention resides in the provision of means controlled by the players to cause the racers to make sprints of different speeds depending on the accumulated amount of reserve energy, and while the racers expend their reserve of energy at normal rate in order to obtain a bonus or at a faster than normal rate.

Another object of the present invention resides in the provision of a racing game of the character described, in which the means to obtain the aforementioned objects may be mechanical or electrical, or both mechanical and electrical.

The foregoing and other important objects of the present invention will become more apparent during the following disclosure and by referring to the drawings, in which:

FIGURE 1 is a schematic top plan view of the racing track in accordance with a first embodiment of the invention;

FIGURE 2 is a cross-section of the racing track of the first embodiment;

FIGURE 3 is a top plan view of the main driving gear wheel of the first embodiment;

3,432,167 Patented Mar. 11, 1969 "Ice FIGURE 4 is a cross-section taken along line 4-4 of FIGURE 3;

FIGURE 5 is a partial crosssection of the main drive gear wheel, together with the transmission from said gear wheel to one racer, the transmission being in a position for making a sprint;

FIGURE 6 is a perspective view, partially in crosssection; of the driving sprocket and part of the shaft therefor;

FIGURE 7 is a cross-section of slow driving pinion assembly;

FIGURE 8 is a perspective view together with its driving shaft of the normal drive pinion assembly;

FIGURE 9 is a perspective view of the spring used for making the overriding clutch in the pinions of FIG- URES 7 and 8;

FIGURES 10, 11 and 12 are partial cross-sections of the main drive gear and of the two pinion assemblies, and showing the three positions of the normal drive pinions, said cross-sections corresponding to that of FIG- URE 5 and FIGURE 10 being a cross-section taken along line Iii-10 of FIGURE 13;

FIGURE 13 is a plan section of the four accumulator assemblies associated with the main drive gear wheel shown in top plan view, each accumulator assembly associated with one racer;

FIGURE 14 is a cross-section taken along line 14-14 of FIGURE 13, but the main drive gear wheel being absent;

FIGURE 15 is a partial perspective of the interlock assembly of FIGURE 14;

FIGURE 16 is a top plan view of the sprint cam and which appears in FIGURES 13, 14 and 24;

FIGURE 17 is a cross-section taken along line 17-17 of FIGURE 14;

FIGURE 18 is a similar cross-section, but in another position of the elements;

FIGURE 19 is a cross-section taken along line 19-19 of FIGURE 17;

FIGURE 20 is a perspective view of a mirror image of the sprint block together with part of the accumulator assembly;

FIGURE 21 is a perspective view of a mirror image of the sprint block looking at the bottom and inner faces thereof;

FIGURE 22 is an elevation of the sprint block;

FIGURE 23 is a top plan view of the sprint block;

FIGURE 24 is a perspective view of a mirror image of the sprint cam plate shown in FIGURE 13;

FIGURE 25 is a partial section taken along line 25-25 of FIGURE 24;

FIGURE 26, shown on the sheet of drawings containing FIGURES 1 and 2, is a plan view of the lever arrangement allowing pulling of one rope at a time of the sprint rope and the accumulator rope;

FIGURE 27 is a top plan view of the top fork for the sprint assembly;

FIGURE 28 is a side elevation of the fork of FIG- URE 27;

FIGURE 29 is a back end elevation of the fork of FIGURE 27;

FIGURE 30 is a partial side elevation of the pivot of FIGURE 27;

FIGURE 31 is a back end elevation of the part of FIGURE 30;

FIGURE 32 is a perspective view of the spring use in the pivot of FIGURE 30;

FIGURE 33 is a top plan view of the lower fork of the sprint assembly;

FIGURE 34 is a side elevation of the fork of FIG- URE 33;

FIGURE 35 is a partial side view of the fork of FIG- URE 33 showing its pivot arrangement;

FIGURE 36 is a cross-section of the parts of FIG- URE 35;

FIGURE 37 is a perspective view of the spring used in the pivot of FIGURE 35;

FIGURE 38 is a top plan view of the upper plate of the accumulator assembly;

FIGURE 39 is an end view of the upper plate of FIGURE 38;

FIGURE 40 is a longitudinal section taken along line 4040 of FIGURE 38;

FIGURE 41 is a top plan view of the lower plate of the accumulator assembly;

FIGURE 42 is a longitudinal section taken along line 42-42 of FIGURE 41;

FIGURE 43 is a top plan view of a portion of the main frame plate in the region of the accumulator assembly;

FIGURE 44 is a longitudinal section taken along line 44-44 of FIGURE 43;

FIGURE 45 is a perspective view of a combined ratchet wheel and cam;

FIGURE 46 is a partial elevation of some of the elements of the sprint and accumulator assemblies;

FIGURE 47 is a cross-section of the main frame plate in the region of the accumulator assembly showing one of the cams working in association with the cams on ratchet wheel of FIGURE 45;

FIGURE 48 is a top plan view of the ratchet wheel and showing its operation;

FIGURES 49, O, 51 and 52 are cross-sections similar to that of FIGURE 14, but with some elements removed and showing the main drive gear wheel, these figures showing the four different positions of the sprint assembly;

FIGURE 53 is an exploded perspective view of a second simpler embodiment in accordance with the invention showing the main drive gear wheel, the accumulator assembly together with the transmission mechanism;

FIGURE 54 is a top plan view of the main drive gear and of three accumulator and driving assemblies associated with said main drive gear and each driving and controlling a racer;

FIGURES 55, 56 and 57 are cross-sections of the main drive gear wheel and accumulator assemblies in three different positions of said accumulator assemblies;

FIGURES 58 and 59 are cross-sections of substantially right angles to the cross-sections of FIGURES 55 to 57 showing two different positions of the accumulator assemblies;

FIGURES 60 and 61 are plan sections of the accumulator assemblies associated with a mechanism for automatic control of a racer between a low and a high set of speeds;

FIGURE '62 is a partial section taken along line 6262 of FIGURE 60; and

FIGURE 63 is a partial section similar of that of FIGURE 62 but in another position, in which the automatic drive is disengaged.

Referring now particularly to the drawings in which like reference characters indicate like elements throughout, the second simpler embodiment illustrated in FIG- URES 53 to 63 inclusive, will first be described.

In both embodiments, there is provided a race track 1 shown in FIGURES 1 and 2, consisting of a board which may be supported on legs 2 and Which may have an oval shape and any other desired shape. Said race track is provided with a plurality of parallel slits 3, each corresponding to the pathway of a racer. In each slit 3 is disposed a flexible ban 4, partially shown in FIG- URE 53, having perforations 5 similar to a movie film engageable by the teeth of tidying sprocket 6 which causes displacement of the endless band 4 within its slit 3.

Each band 4 is fitted with the representation of a racer, such as a horse, as shown at 7 in FIGURE 5. The figurine 7 may be removably clipped on the endless band 4. Each band 4 is driven by its sprocket 6, and all the sprockets are in turn driven by a mechanism housed underneath a portion of the race track 1 in accordance with the second embodiment.

Referring to FIGURE 53, the driving mechanism comprises a common main driving wheel 8 driven at a constant speed of rotation by any suitable means such as an electric motor driving a worm meshing with external gear teeth (not shown) on the gear wheel 8, as in the embodiment shown in FIGURE 1.

Gear Wheel 8 has on the outside three gear sectors 9, 10 and 11 of increasing diameter and each extending through one-third of a circle so that one sector ends where the next sector of the series starts. The gear sectors 3, 10 and 11 therefore come in successive engagement with the respective pinions 12, 13 and 14 of decreasing diameter and all secured to a common shaft 15. Said shaft 15 drives the shaft 16 of the sprocket 6 through an overriding clutch 17, where-by shaft 16 may be driven at higher speed than shaft 15.

Shaft 16 is provided with a gear wheel 18. Sprocket 6 has an internal friction clutch whereby the racer or horse 7, together with its band 4, may be stopped by hand or otherwise while the driving mechanism is operating.

Main gear 8 has furthermore three internal gear sectors 19, 20 and 21 of progressively increasing diameter and each extending through one-third of a circle and such that one sector ends where the next sector of the series starts.

Gear sectors 19, 20 and 21 are adapted to come successively in meshing engagement with the respective three pinions 22, 23 and 24 of progressively increasing diameter and all mounted on a common shaft 25.

An additional smaller diameter accumulator pinion 26 is mounted on shaft 25 on top of pinion 24 and is free of any engagement with the main gear 8 when the pinions 22, 23 and 24 are in engagement with gear sectors 19, 20 and 21.

However, upon bodily displacement of the pinions 22, 23 and 24, pinion 26 comes into engagement with an accumulator gear sector 27 formed for about one-third of the periphery of a central flange 28 integral with gear wheel 8. Accumulator gear sector 27 is preferably disposed opposite gear sector 11, as shown in FIGURE 54, said gear sector giving the highest of the slow speeds. Sector 27 is also preferably disposed opposite internal gear sector 19, which is the highest of the normal speeds, although sector 27 could be disposed opposite sector 21, the lowest normal speed, as shown in FIG- URE 54.

Shaft 25 carrying pinions 22, 23, 24 and 26 is journalled at 25' in an upper plate 29 and freely passes through a hole 30 of a lower plate 31 and also through a hole of the framework plate 32 of the machine (sec FIGURES 55 to 57), said plate 32 overlying gear wheel 8 and underlying plates 29 and 31.

The plates 29 and 31 are of rectangular shape, are superposed and are bodily pivotable as a unit about a pivot screw 33 secured to the framework plate 32.

This pivot pin 33 is spaced from shaft 25. Thus, by pivoting the upper plate 29 about pivot pin 33, the gears 22, 23 and 24 may be made to engage or disengage the associated gear sectors 19, 20 and 21, as shown in FIG- URES 55 and 56 and may also be further pivoted in wardly so that the accumulator pinion 26 will engage the accumulator gear sector 27, as shown in FIGURE 57.

This movement is effected by means of a draw rope 34 attached to the lower plate 31 and controlled by the player.

Up n release f r pe 34 hich c r e ponds o a rein for a horse, a tension coil spring also attached to the lower plate 31 and to the framework, will pivot the lower plate 31 so that pinions 22, 23, 24 will normally be in contact with internal gear sectors 19, 20, 21.

Plate 29 is also pivotable with respect to the lower plate 31 about pivot pin 33 under action of a tension coil spring 36 attached to the upper plate and to the frame work. However, the coil spring 36 has less strength than coil spring 35 so that when the two plates 29 and 31 are interlocked, the coil spring 35 will move the assembly of the two plates 29 and 31 against the action of spring There is provided, as above-mentioned, an interlock between the two plates 29 and 31. Said interlock includes an upright plunger 37 freely displaceable in a bushing 38 secured to the upper plate 29 and resting at its lower end on a stud 39 upstanding from the outer end of a leaf spring 40 carried by the lower plate 31.

Each spring 40 normally maintains stud 39 against the Weight of plunger 37 in a position extending into a hole made in the upper plate 29 so as to lock the two plates 29 and 31 against relative pivotal movement. However, upon downward movement of plunger 37, the stud 39 is pushed downwardly so as to clear the upper plate 29, as shown in FIGURE 5 6, whereupon the upper plate may pivot with respect to lower plate 31 under action of coil spring 36.

A gear wheel 41 is secured to shaft 25 above upper plate 29 at the level of gear wheel 18 on shaft 16 so as to mesh with the same when pinions 22, 23, 24 are in meshing engagement with internal gear sectors 19, 20, 21, as shown in the position of FIGURE 55.

The part of the shaft 25 above gear wheel 41 is threaded and is provided at its upper end with a flattened portion 42 slidably engaged by a head 43 which is rotatable along with shaft 25, but which may be vertically adjusted, as shown by its position in dotted line in FIGURE 55, by means of a setting screw 44 screwed within the top framework plate of the mechanism housing, not shown, and provided at its lower end with a fork 45, rotatably engaging a groove made at the periphery of head 43, so as to allow rotation of the head 43 with respect to the fork but maintaining the head at the desired level.

Head 43 is slidable over the thread of shaft 25 and carries a ball 46 engaging with the flat 42 to prevent rotation of head 43 with respect to shaft 25. Head 43 has downwardly extending pin 47 while gear wheel 41 has an upwardly extending pin 48.

Intermediate the head 43 and gear wheel 41, there is screwed on shaft 25 a cursor wheel 49 having a double flange between which is rotatable a cursor arm 50 having a forked outer end 51 engaging a rod 52 forming a cursor arm guide which is secured to the top plate 29 in upright position.

Cursor arm 30 is thus prevented from rotation by the guide rod 52 and, therefore, it normally prevents rotation of the cursor wheel 49 during rotation of spindle 25, due to the friction between the two flanges of the wheel 49 and the curved spring-like portion 53 of the arm 50. Thus, rotation of shaft 25 will cause up or down movement of the cursor wheel 49 along shaft or spindle 25 until the upper or lower stop pin 55 carried by the cursor wheel 49, will engage the top pin 47 or the stop pin 48 of head 43 and gear wheel 41 respectively, at the topmost and lowermost limit positions of the range of movement of the cursor wheel 49 along shaft 25.

In these two limit positions, the cursor wheel 49 will be brought into rotation along with shaft 25 and will therefore remain in abutment either with head 43 or with gear wheel 41.

By adjusting the vertical position of head 43, it will be appreciated that the range of up-and-down movement of the cursor wheel 49 may be increased or decreased so as to store more or less energy in the accumulator system.

When cursor arm 50 moves down, it will finally abut the upper end of plunger 37 which acts as a detent to release the interlock formed by the stud 39 and thereby allows pivotal movement of the upper accumulator plate 29 with respect to the lower accumulator plate 31 under the action of spring 36.

The system operates as follows:

It will be understood that all the mechanism is enclosed in a housing so as to be hidden from view and only the rope 34 is accessible to each player. Each player controls one racer or horse 7. Gear wheel 8 actuates all the recess 7, each racer being associated with an accumulator assembly and driving assembly.

Referring to FIGURE 1, there is provided a starting gate 56 disposed across the race-track 1 and held in position until all the racers or horses 7 abut against the same. It should be remembered that each sprocket 6 is provided with a friction clutch which allows to hold the horses stationary against the starting gate while the shafts 16 of the sprockets are rotating.

At the start of the race, all the accumulators will be charged, that is the cursor wheels 49 will be at their top limit position in engagement with the respective head 43. This can be accomplished by allowing the horses 7 to move once around the track 1 while retained at the slow speeds, as will be later described.

A race may consist of two turns around track 1 corresponding to about ten turns of main gear wheel 8.

The starting gate 56 is removed and the horses start to move along the race-track. The draw ropes 34 being released, the horses will run in their normal range of speed while gradually depleting or using up their reserve of energy.

In this normal range of speed, the accumulator assembly is in position A, as shown in FIGURES 54, 55 and 58. The pinions 22, 23, 24 successively engage the internal gear sectors 19, 20 and 21, thereby rotating shaft 25 and, consequently, gear wheel 41 in a direction to cause gradual lowering of cursor wheel 49, thereby depleting the reserve of energy.

Gear wheel 41 in turn drives gear wheel 18 in opposite direction, which is driven at a faster speed than shaft section 15, thus driving shaft 16 at a high speed, due to the presence of overriding clutch 17. Thus, sprocket 6 drives the associated band 4 within a range of normal speeds, namely: three different speeds in accordance with the ratios of pinions 22, 23, 24 with respect with internal gear sectors 19, 20 and 21.

When the reserve of energy is depleted, that is when gear cursor wheel 49 attains its lower limit position abutting against the gear wheel 41, the cursor arm 50 pushes down on plunger 37, as shown in FIGURE 56, thereby releasing the interlock between the upper and lower accumulator plates 29 and 31 of the accumulator assembly, automatically moving pinions 22, 23 and 24 inwardly out of engagement with the internal gear sectors 19, 20 and 21, as shown at position B in FIGURES 54, 56 and 59. In this position, the external pinions 12, 13 and 14 become active to drive the associated sprocket 6 and horses 7 at a lower range of speeds, meaning that the reserve of energy having been spent, the horse moves automatically at slow speeds.

The inward movement of shaft 25 has caused disengagement of the gear wheels 18 and 41, as shown in FIGURE 56.

To replenish the reserve of energy, the player must pull on draw rope 34. This moves the accumulator assembly to position C, shown in FIGURES 54 and 57. In this position, pinions 22, 23, 24 remain free of engagement with gear sectors 19, 20 and 21 but accumulator pinion 26 meshes with accumulator gear sector 27 and is rotated for one-third of every revolution of the main gear wheel 8. Thus, shaft 25 is rotated in a direction opposite to its direction of rotation when in position A, whereby the cursor wheel 49 is caused to rise along the threaded portion of shaft 25, thereby accumulating energy.

The rising accumulator wheel releases the plunger 37, allowing stud 39 to interlock the top and bottom accumulator plates 29 and 31. Thus, when a certain amount of energy has been stored in the accumulator, that is when the position of the cursor wheel 49 is sufficiently high to clear the plunger 37, the accumulator assembly may be returned to the normal fast speed range, that is position A, by releasing the draw rope 34.

The player must develop skill in handling his racer; he must not put the mechanism in accumulating position C for too long a time, because no more accumulation of energy takes place when the cursor wheel 49 has reached its upper limit position abutting against head 43. The player must learn to accumulate energy at the most appropriate time, that is when the racer would otherwise run at the highest of the slow speeds, because recuperating gear sector 27 is opposite slow speed gear sector 11. This can be more easily effected by keeping always a reserve of energy in the accumulator system; otherwise, the player would be forced to run his horse on the slowest and intermediate slower of the slow speeds while trying to recuperate.

From the foregoing, it will be noted that it is to the advantage of the player never to allow the accumulator system to become completely run down.

FIGURES 60 to 63 show an automatic cam arrangement that can take over the operation of one or more racers in the absence of a corresponding number of players and still afford competition to the other players.

An actuator arm 57 is secured to the housing of the overriding clutch 17 between shaft and shaft 16 and is engageable with ratchet pins 58 during rotation of shaft 16, said ratchet pins 58 depending downwardly from a cam plate 59 provided with one or more notches 60 at its periphery.

A finger 61, secured to and upstanding from the side of the upper accumulator plate 29, rides on the periphery of cam plate 59 so that, when it engages notch 60, the upper plate 29 will pivot with respect to the lower plate 31 under action of spring 36.

For this purpose, the interlock between the top and bottom accumulator plates 29 and 31 must be disengaged so as to allow free pivotal movement of the top plate 29 and, therefore, the accumulator must be empty, that is the cursor arm must push down on the plunger 37. With this arrangement, the top plate 29 will pivot under the action of the cam wheel 59 to thereby successively run the horses between fast and slow speeds.

Means are provided to manually place the automatic system into and out of operation. For this purpose, the shaft 62 on which the cam plate 59 is secured, is provided at its top end with a manually-operated knob 63 and is surrounded just below knob 63 by a coil spring 64 freely extending, together with shaft 52, through a hole made in framework plate 65.

The lower end of spring 64 abuts against a frame extension 66 through which only the shaft 62 passes.

An L-shaped finger 67 depends from knob 63 and is adapted to extend through an L-shaped notch 68 made in the framework plate so as to engage underneath the same and retain the shaft 52 and also the cam plate 59 in lowered position against the action of spring 64.

Upon rotation of knob 63, L-shaped finger 67 will clear notch 68 and the shaft 62 will be urged into an elevated position with the ratchet pins 58 clearing the actuator arm 57, as shown in FIGURE 63, for the nonautomatic operation of the racer.

FIGURES and 61 show also that upper plate pivot ing spring 36 can be replaced by a hair pin spring 36'.

FIGURES 1 to 52 inclusive show the first embodiment of the invention, which is more complex than the second embodiment just described, provision being made for making sprints, that is for running the racers at a higher set of speeds than the normal speeds for certain times during the race and depending on the state of the accumulator system, it being impossible to make the sprints when the accumulator system is depleted and at certain other times during the race.

A main gear wheel 70, shown in FIGURES 3 and 4, is provided on the outside with concave gear teeth 71 meshing with a worm 72 (see FIG. 1), driven by an electric motor 73.

The outside of gear wheel 70 is provided with three gear sectors 74, 75, 76, of progressively increasing diameter, each extending through one-third of a circle and each sector starting at the end of the next sector.

Gear sectors 74, 75, 76 therefore successively mesh with the three respective pinions 77, 78, 79 (see FIGURE 5) of progressively decreasing diameter and secured to a shaft 80 journalled in the frame of the machine and vertically arranged and provided at its lower end with a bevelled pinion 81 driving bevelled pinion 82, in turn driving through shaft 83, bevelled pinion 84 which drives bevelled pinion 85 secured to the lower end of drive shaft 86, on the upper end of which is mounted a sprocket wheel 87 having a friction clutch therein, whereby the sprocket 87 can be stopped from rotating even when drive shaft 86 is rotating.

Sprocket 87 drives perforated flexible band 88 in a slit 3 of race-track 1 of FIGURE 1. A racer or horse 7 is clipped on each band 88.

With the driving arrangement just described, the entire mechanism can be located in a box 1' inside the race-track 1 proper, as shown in 'FiIGUR'E 1, so that the race-track 1 will have a minimum height. The three pinions 77, 78 and 79 form an integral unit provided with an overriding clutch, indicated at 89, and simply consisting of a wire having a straight leg extending through a hole 90 of the shaft 80 and a curved portion terminated by a tooth 91 frictionally engaging the inside groove 92 of the pinion assembly and allowing free rotation of the pinion assembly in one direction, while locking the same on the shaft 86 in the other direction. This overriding clutch allows the shaft 80 to rotate at a faster rate than the pinion assembly 77, 78, 79.

Main gear wheel 70 is further provided, as in the first embodiment, with three gear sectors 93, 94, 95, of progressively increasing diameter, and each extending through one-third of a circle, one smaller diameter sector terminating at the start of the next larger diameter sector.

Pinions 96, 97, 98, of progressively increasing diameter, mesh respectively and successively with the gear sectors 93, 94, 95, as in the first embodiment. The pinions 96, 97, 98 form a unit, as shown in FIGURE 8, and is provided with an overriding clutch 89 on the shaft 99 supporting said pinions. Clutch 89' is similar to clutch 89.

Main gear wheel 70 has also a recuperating or accumulator gear sector 100, as in the first embodiment, the teeth of which project outwardly from a central flange 101 of the gear wheel 70 through about one-third of a circle. This gear is adapted to mesh with a pinion 162 keyed to shaft 99. Gear 100 is preferably disposed opposite the highest speed sectors 76 and 93.

An additional gear sector 103 used for Sprints, is made on the inside of main gear wheel 70 and extends also for approximately one-third of a circle and serves for the sprint transmission. Gear sector 103 is disposed opposite the lowest normal speed gear sector 95. Gear sector 103 is adapted to mesh with a slidable pinion 104 mounted on shaft 99. Pinion 104- has a flange 105 and a pin which is adapted to slide in a slot 106 of shaft 99 so as to prevent rotation of the pinion with respect to the shaft while allowing up-and-down movement of said pinion on the shaft.

Similarly, top and bottom driving gears 167, 108, of larger and smaller diameters, form a unit provided with a 9 flange 109 and said unit is slidable on the shaft 99, but is rotated thereby by means of a pin integral with the gear assembly and riding in a slot 110' of the shaft 99.

Gears 107, 108 are adapted to mesh with top and bottom driven gears 1111, 112 respectively, which are spaced from one another, and keyed to shaft 80.

In the raised position of gears 107, 108, shown in FIGURE 5, the top gears 107, 111 are in meshing engagement while the bottom gears 108, 112 are out of engagement.

In the lowered position of the gear assembly 107, 108, top gears 107, 111 will be out of engagement while bottom gears 108 and 112 will be in meshing engagement, provided shaft 89 is in the position in FIGURE 5, with pinions 96, 97 and 98 engaging the inside gear sectors 93, 94, 95.

Sprint gear sector 103 is of smaller diameter than the smallest inside gear sector 93. In the position (2-11 of FIGURE 49, there is no multiplication of speed. In this position, the top gear assembly 107, 108 is in lowered position with the bottom gear 180 engaging the bottom gear 112. Also, the sprint gear sector 103 is out of engagement with the slidable pinion 104, the latter being in raised position.

In the position b-b of FIGURE 50, the top gear assembly 107, 108 is in lowered position, as in FIGURE 49, but the sprint gear sector 103 is in engagement with the lowered pinion 104. Thus, said lowered pinion drives the shaft 99 at an increased speed with respect to the maximum speed obtainable from gear sector 93 and pinion 96. Thus, position b--b corresponds to the position of a first additional speed with respect to the normal maximum speed.

In position cc of FIGURE 51, the top gears 107, 108 are in raised position, thereby driving shaft 80 at a higher speed than in the positions a-a and bb. However, the shaft 99 rotates at the same speed as in position a-a, slidable pinion 104 being out of engagement with sprint sector 103. Thus, the shaft 99 rotates at the same speed as in normal operation. Thereby, the accumulator will be expended at the same rate as in normal op eration, however, with a gain of speed, so this is a bonus speed position.

In position d-d of FIGURE 52, the top gear assembly 107, 108 is still in raised position; however, the slidable pinion 104 is in engagement With the sprint sector 103. Thus, this position corresponds to the maximum speed ohtainable with the shaft 99 rotating at an increased speed, which results also in a faster rate of expenditure of the accumulated energy.

Gear assembly 107, 108 is moved up and down by a top fork 113 engaging the flange 109 and pivoted at 114 to a bracket 115 secured to the top plate 116 of the accumulator assembly. The lower slidable pinion 104 is moved up and down by a bottom fork 117 rotatably engageable with the flange 105 of pinion 104 and pivoted at its other end at 118 to the underside of top plate 116 of the accumulator assembly.

The pivots 114 and 118 are provided with springs 119 and 120 respectively (see FIGURES 30, 31, 32, 35, 36, 37) urging the fork 113 in downward position and the fork 117 in upward position, so as to normally maintain the gears 107, 108 in lowered position and slidable pinion 104 in raised position respectively, which is position aa of FIGURE 49.

A cam plate, more particularly shown in FIGURES 13, 14, 16, 24 and also in FIGURES 49 to 52 and generally indicated at 121, is mounted in a horizontal position for adjusted rotation about shaft 99 so as to take four positions engaging the inwardly extending fingers 122, 123 of the top and bottom forks 113, 117 respectively so as to position said forks in the four respective positions shown in FIGURES 49, 50, 51 and 52.

Cam plate 121 may be rotated to take four positions by means of a draw rope 124 attached thereto and directly accessible to the player, as shown in FIGURE 13. Cam plate 121 in its rotated position in which zone a of FIGURE 16 is opposite the fingers 122 and 123 of the forks 113 and 114, corresponds to the position aa of FIGURE 49, the fingers of said forks directly contacting the top and bottom surfaces of the cam plate In the rotated position of cam 121 wherein zone b thereof is opposite fingers 122, 123, the finger 123 engages a bottom boss 125 of the cam plate, thereby lowering fork 117, which corresponds to position [2-]; shown in FIGURE 50.

When thecam plate 121 is rotated to a third position in which zone c is engaged by the fingers 122, 123, the finger 122 is raised by the top boss 126 of the cam plate. This position corresponds to position cc of FIGURE 51. Finally, when the cam plate 121 is rotated so that its zone d is opposite the fingers 122-123, the top finger 122 still engages the top boss 126 while the bottom finger 123 engages a boss 127 at the underface of the cam plate, whereby both forks 113, 117 are pivoted outwardly corresponding to the position d-d of FIGURE 52.

A coil spring 132, shown in FIGURES 14 and 46, normally returns the cam plate 121 in the position a-a (FIG. 49), in which the fingers 122-123 are opposite zone a of the cam, as shown in FIGURE 16.

The cam can be rotated by draw rope 124 to the positions b-b, 0-0 or d-d only under certain conditions, that is depending on the state of charging of the accumulator system and for certain portions of the rotational cycle of the main gear wheel 7 0.

The accumulator system is similar to that of the first embodiment: apart from the top plate 116, there is a bottom accumulator plate 128 positioned underneath the top plate 115 and both plates are pivoted horizontally about pivot pin 129 so as to move with respect to the frame plate 130.

There is an interlock system comprising plunger 131 guided in tube 131' secured to top plate 116, and a spring detent, the leaf spring 133 of which is secured to the bottom accumulator plate 128 and has at its free end a steel ball 134 normally engaging between the two plates 116, 128 to lock the same together, but releasing these two plates for relative pivotal movement thereof under downward movement of plunger 131.

Shaft 99 is journalled in bushing 116' of top plate 116 (FIGURE 40) and can move freely in opening 128' of bottom plate 128 (FIGURE 41), and in notch of framework plate 130 (FIGURE 43). Bushing 116 serves also as a pivot for cam plate 121 and as anchor for the inner end of return spring 132.

The shaft 99 has an upper threaded portion 99' on which is screwed a cursor wheel 135 having two spaced flanges between which is located the inner end of a cursor arm 136, the outer end of which is forked and is guided by guide pin 137 secured in upright position to the top accumulator plate 116.

As in the first embodiment, cursor wheel 135 has two oppositely directed pins 138 adapted to engage respectively the bottom pin 139 of wheel 140 secured to shaft 99 and pin 141 of head 142 secured to the top of shaft 99. As in the first embodiment, said head may be level-adjusted to establish odds, if so desired.

As in the first embodiment, when the cursor wheel 135 abuts against the head 142, it starts to rotate with the shaft and thus remains in upper limit position. Inversely, when the cursor wheel 135 abuts against the top wheel 138, it starts to rotate with the shaft and, therefore, remains in its lower limit position. In this lower limit position, the cursor arm 136 moves plunger 131 downwardly, thereby releasing the interlock between the two accumulator plates 116, 128 to automatically move the normal speed pinions 96, 97, 98 out of engagement with the inside gear sectors 93, 94, 95 of main gear wheel 70, upper plate 116 being rotated inwardly relative to 

